US8584457B2 - Cooler arrangement for a vehicle powered by a supercharged combustion engine - Google Patents

Cooler arrangement for a vehicle powered by a supercharged combustion engine Download PDF

Info

Publication number
US8584457B2
US8584457B2 US13/699,319 US201113699319A US8584457B2 US 8584457 B2 US8584457 B2 US 8584457B2 US 201113699319 A US201113699319 A US 201113699319A US 8584457 B2 US8584457 B2 US 8584457B2
Authority
US
United States
Prior art keywords
cooler
cooling
cooling circuit
coolant
medium
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US13/699,319
Other languages
English (en)
Other versions
US20130068202A1 (en
Inventor
Zoltan Kardos
Kristoffer Klingberg
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Scania CV AB
Original Assignee
Scania CV AB
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Scania CV AB filed Critical Scania CV AB
Assigned to SCANIA CV AB reassignment SCANIA CV AB ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KARDOS, ZOLTAN, KLINGBERG, Kristoffer
Publication of US20130068202A1 publication Critical patent/US20130068202A1/en
Application granted granted Critical
Publication of US8584457B2 publication Critical patent/US8584457B2/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/20—Cooling circuits not specific to a single part of engine or machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
    • F01P7/165—Controlling of coolant flow the coolant being liquid by thermostatic control characterised by systems with two or more loops
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F02B29/0412—Multiple heat exchangers arranged in parallel or in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • F02G5/04—Profiting from waste heat of exhaust gases in combination with other waste heat from combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/18—Arrangements or mounting of liquid-to-air heat-exchangers
    • F01P2003/187—Arrangements or mounting of liquid-to-air heat-exchangers arranged in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P2060/00—Cooling circuits using auxiliaries
    • F01P2060/02—Intercooler
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P2060/00—Cooling circuits using auxiliaries
    • F01P2060/16—Outlet manifold
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2260/00—Recuperating heat from exhaust gases of combustion engines and heat from cooling circuits
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to a cooler arrangement for a vehicle which is powered by a supercharged combustion engine.
  • EGR exhaust gas recirculation
  • US 2009/0211253 refers to an energy recovery arrangement whereby a circulating medium absorbs thermal energy from a plurality of heat exchangers in the form of, inter alia, a charge air cooler and an EGR cooler.
  • the medium is warmed by the thermal energy absorbed to a temperature at which it vaporises.
  • the vaporised medium has not only a raised temperature but also a raised pressure.
  • the medium is then led through a turbine. Part of the thermal energy absorbed is converted in the turbine to mechanical energy.
  • the medium is led thereafter to a condenser in which it is cooled by a cooling air flow to a temperature at which it condenses.
  • the resulting liquid medium is circulated from the condenser back to said coolers in order to again absorb thermal energy so that it becomes vaporised.
  • the object of the present invention is to reduce the fuel consumption of a vehicle which is powered by a supercharged combustion engine.
  • the amount of air led into a combustion engine is related to the engine's performance and fuel consumption.
  • a cooler arrangement which comprises three cooling circuits with coolant at different temperatures.
  • the third cooling circuit which has coolant at the lowest temperature, may here be used to cool the compressed air in a charge air cooler.
  • the compressed air may thus be cooled to a very low temperature before it is led to the combustion engine.
  • Such cooling makes it possible for a large amount of air to be led to the combustion engine, resulting in low fuel consumption.
  • the vehicle has an energy recovery system containing a phase-transforming medium which absorbs thermal energy from suitable heat sources close to the combustion engine. Normally this thermal energy is not utilised but is released to the surroundings.
  • the medium which may be water, has the characteristic that it vaporises at a lower temperature than the temperature of at least one of said heat sources.
  • the vaporised medium thus acquires a raised pressure and a raised temperature.
  • the vaporised medium is led to a turbine which converts part of the medium's thermal energy to mechanical energy.
  • the medium is thereafter cooled in a condenser to a temperature at which it reverts to liquid form.
  • coolant in the third cooling circuit may be used to cool the medium in a condenser.
  • the medium may thus be cooled to a temperature close to the temperature of the coolant in the third cooling circuit.
  • the coolant in the third cooling circuit may be used to cool the air or the medium which is not cooled by the coolant in the third cooling circuit.
  • the first cooler, the second cooler and the third cooler are situated in a region of the vehicle where a substantially common cooling air flow passes through them and they are so arranged that the second cooler is situated upstream of the first cooler and the third cooler is situated upstream of the second cooler with respect to the intended direction of air flow through the coolers.
  • the air led through said coolers thus acquires progressively rising temperature as it cools the coolants in the respective coolers.
  • the coolant in the third cooler will be cooled to the lowest temperature. Since the air reaching the second cooler is at a lower temperature than the air reaching the first cooler, the coolant in the second cooler acquires a lower temperature than the coolant in the first cooler.
  • the third cooler is with advantage so located in the vehicle that it has air at the temperature of the surroundings flowing through it.
  • the coolant in the third cooler may thus be cooled to a temperature close to the temperature of the surroundings. Consequently, the compressed air and/or the phase-converting medium may also be cooled by the coolant in the third cooler to a temperature close to the temperature of the surroundings.
  • the first cooling circuit, the second cooling circuit and the third cooling circuit form part of a common cooling system.
  • a coolant pump can circulate the same coolant through all three circuits.
  • the configuration of this common cooling system may preferably be such that the coolant in the third cooling circuit has undergone three steps of cooling before it is used for cooling the compressed air and/or the medium.
  • the coolant is first cooled in the first cooler, thereafter in the second cooler and finally in the third cooler.
  • the coolant in the third cooling circuit may thus acquire effective cooling to a low temperature.
  • the first cooling circuit may constitute a separate cooling system and the second cooling circuit and the third cooling circuit may jointly constitute another cooling system.
  • a coolant pump circulates coolant in the first cooling circuit.
  • Another coolant pump circulates coolant in the cooling system which comprises the second cooling circuit and the third cooling circuit.
  • the first cooling circuit, the second cooling circuit and the third cooling circuit constitute three separate cooling systems. In this case a coolant pump is required in each of the three separate cooling systems.
  • the energy recovery system comprises two condensers and the coolant in the second cooling circuit is used to cool the medium in a first condenser and the coolant in the third cooling circuit is used to cool the medium in a second condenser which is situated downstream of the first condenser.
  • the cooling of the medium is important for achieving good absorption of thermal energy in the heat recovery system. It may therefore be necessary to subject the medium to two steps of cooling in two separate condensers. In this case it is advantageous to use the coolant in the second cooling circuit to subject the medium to a first step of cooling and the coolant in the third cooling circuit to subject the medium to a second step of cooling.
  • the energy-absorbing system comprises with advantage at least one heat exchanger in which the medium is intended to absorb thermal energy from a heat source in the form of warm coolant, compressed air, exhaust gases in the exhaust line or recirculating exhaust gases. All of these heat sources contain surplus heat which can be utilised in the energy recovery system.
  • the coolant, the compressed air and the recirculating exhaust gases are normally cooled in at least one cooler to lower their temperature, in which case the heat exchanger may replace or complement such an ordinary cooler.
  • the vehicle comprises a return line for recirculation of exhaust gases and the recirculating exhaust gases are cooled in an EGR cooler by coolant from the third cooling circuit or by the medium after it has been cooled by the coolant in the third cooling circuit in the condenser.
  • coolant In cases where exhaust gases are added to the compressed air which is led to the combustion engine, it is advantageous to cool the recirculating exhaust gases to the same low temperature as the compressed air. It is therefore appropriate to use the coolant in the third cooling circuit for this purpose.
  • the medium may be used to similar effect after it has been cooled by the coolant in the third cooling circuit.
  • the first cooling circuit contains with advantage coolant which is used for cooling the combustion engine.
  • the operating temperature of this coolant should normally be about 70-90° C. to cool the combustion engine to a suitable temperature.
  • the coolant in the first cooling circuit, the second cooling circuit and the third cooling circuit may of course be used to meet other cooling requirements in the vehicle. Since the coolant will be at different temperatures in the three cooling circuits, the coolant which is at the most suitable temperature may be used in each case.
  • FIG. 1 depicts a cooler arrangement for a supercharged combustion engine according to a first embodiment of the invention
  • FIG. 2 depicts a cooler arrangement for a supercharged combustion engine according to a second embodiment of the invention
  • FIG. 3 depicts a cooler arrangement for a supercharged combustion engine according to a third embodiment of the invention.
  • FIG. 1 depicts a supercharged combustion engine adapted to powering a schematically depicted vehicle 1 which may be a heavy vehicle 1 .
  • the combustion engine 2 is here exemplified as a diesel engine 2 .
  • the exhaust gases from the cylinders of the diesel engine 2 are led to an exhaust line 4 via an exhaust manifold 3 .
  • the diesel engine 2 is provided with a first turbo unit which comprises a turbine 5 and a compressor 6 .
  • the exhaust gases in the exhaust line 4 expand through the turbine 5 , which is thus provided with driving power which is transmitted, via a connection, to the compressor 6 .
  • the arrangement comprises an inlet line 8 adapted to leading air to the combustion engine 2 .
  • the compressor 6 of the first turbo unit compresses air which is drawn into an inlet line 8 via an air filter 7 .
  • the air undergoes a first step of cooling in a first charge air cooler 9 and a second step of cooling in a second charge air cooler 10 .
  • the arrangement comprises a return line 11 for recirculation of exhaust gases from the exhaust line 4 .
  • the return line 11 has an extent between the exhaust line 4 and the inlet line 8 .
  • the return line 11 comprises an EGR valve 12 by which the exhaust flow in the return line 11 can be shut off.
  • the EGR valve 12 may also be used to steplessly control the amount of exhaust gases led from the exhaust line 4 to the inlet line 8 via the return line 11 .
  • a control unit 13 is adapted to controlling the EGR valve 12 on the basis of information about the current operating state of the diesel engine 2 .
  • the return line 11 comprises a first EGR cooler 14 for subjecting the recirculating exhaust gases to a first step of cooling, and a second EGR cooler 15 for subjecting the exhaust gases to a second step of cooling.
  • the compressed air and the recirculating exhaust gases are mixed in a portion 16 before they are led to the respective cylinders of the diesel engine 2 via a manifold 17 .
  • the vehicle 1 is in this case provided with a cooler arrangement in the form of three cooling circuits containing coolant at different temperatures.
  • the coolant is circulated in the cooler arrangement by a coolant pump 18 .
  • the configuration of a first cooling circuit of the cooler arrangement corresponds substantially to a conventional cooling system for cooling a combustion engine 2 .
  • the first cooling circuit comprises a line system 21 which leads coolant through the combustion engine 2 . After it has cooled the combustion engine 2 , the coolant is led to a further cooler which may be an oil cooler 22 for a retarder. After it has cooled the oil in the oil cooler 22 , the coolant is led to a thermostat 19 .
  • the thermostat 19 directs the coolant to the combustion engine 2 in situations where it has not reached a necessary operating temperature, or to a first cooler 20 for cooling when it needs cooling.
  • the first cooler 20 is situated close to a forward portion of the vehicle 1 .
  • a radiator fan 23 forces a cooling air flow through the first cooler 20 . After being cooled in the first cooler 20 , the coolant is led back to the combustion engine 2 .
  • a second cooling circuit of the cooler arrangement comprises a second line system 24 .
  • the line system 24 receives part of the coolant from the first line system 21 at a location 25 situated immediately downstream of the coolant pump 18 . Coolant has undergone a first step of cooling in the first cooler 20 when it reaches the location 25 .
  • the coolant in the second cooling circuit is led in the line system 24 to a second cooler 26 in which it undergoes a second step of cooling.
  • the second cooler 26 is situated upstream of the first cooler 20 with respect to the direction of cooling air flow through the coolers 20 , 26 . This means that the coolant in the second cooler 26 is cooled by air which is at a lower temperature than the air which flows through the first cooler 20 .
  • the coolant in the second cooler 26 thus acquires a lower temperature than the coolant which is cooled in the first cooler 20 .
  • the second cooling circuit comprises at a location 27 a connection to the third cooling circuit.
  • the third cooling circuit of the cooler arrangement comprises a line system 28 which receives part of the coolant from the second cooling circuit at a location 27 .
  • This coolant has therefore undergone a first step of cooling in the first cooler 20 and a second step of cooling in the second cooler 26 .
  • the coolant is led in the line system 28 to a third cooler 29 situated upstream of the second cooler 26 and the first cooler 20 with respect to the direction of air flow through the coolers 20 , 26 , 29 .
  • the coolant leaving the third cooler 29 is therefore at a lower temperature than the coolant leaving the second cooler 26 .
  • the third cooler 29 is situated at a location in the vehicle 1 where it is in contact with air at the temperature of the surroundings.
  • the coolant in the third cooler 29 may therefore be cooled to a temperature close to the temperature of the surroundings.
  • the coolant in the third cooling circuit is led back to the second cooling circuit at a location 30 . Coolant from the second cooling circuit is thereafter led back to the first cooling circuit at a location 31 .
  • the combustion engine 2 is provided with an energy recovery system.
  • the energy recovery system comprises a line circuit 32 with a circulating medium which has a suitable vaporisation temperature.
  • the medium is with advantage water.
  • the medium is circulated in the circuit 32 by a pump 33 .
  • the medium is led in liquid form by the pump 33 to a first heat exchanger 34 .
  • the medium is warmed in the first heat exchanger 34 by the coolant in the first cooling circuit.
  • the coolant may here be at a temperature of up to about 100° C.
  • the medium is thereafter led to a second heat exchanger which here takes the form of a first charge air cooler 9 .
  • the compressed air may be at a temperature of up to about 200° C.
  • the medium may be wholly or partly vaporised in the charge air cooler 9 when it is heated by the compressed air.
  • the medium is then led to a third heat exchanger 35 in which it is heated by the exhaust gases in the exhaust line 4 .
  • the exhaust gases which have here expanded through the turbine 5 may be at a temperature of up to about 350° C.
  • the medium, which is now in a wholly vaporised state, is warmed finally in a fourth heat exchanger in the form of the first EGR cooler 14 .
  • the recirculating exhaust gases may be at a temperature of up to about 650° C.
  • the medium undergoes in the first EGR cooler 14 a fourth step of warming to a relatively high temperature and a relatively high pressure.
  • the line circuit 32 comprises downstream of the fourth heat exchanger 14 a valve 36 which can direct the medium to a turbine 37 or to a bypass line 38 .
  • the vaporised medium is normally led to the turbine 37 , in which it expands.
  • the turbine 37 thereby acquires rotary motion which is transmitted, via a mechanical transmission 39 , to the flywheel 40 on an output shaft 41 from a gearbox 42 which is connected to the combustion engine 2 .
  • the output shaft 41 thereby acquires extra driving power to propel the vehicle 1 .
  • the mechanical transmission 39 may comprise a suitable number of motion-transmitting elements in the form of spur gears or the like so that the motion from the turbine 37 undergoes a suitable downshift before it is transmitted to the flywheel 40 .
  • the bypass line 38 has a first end connected to the line circuit 32 at a location upstream of the turbine 37 and a second end connected to the line circuit 32 at a location downstream of the turbine 37 with respect to the direction of flow of the medium in the line circuit 32 .
  • the valve 36 may thus be placed in a first position whereby it leads the vaporised medium to the turbine 37 and in a second position whereby it leads the medium through the bypass line 38 and consequently past the turbine 37 .
  • the medium may be led through the bypass line 38 in situations, for example, where the medium has not been completely vaporised or where the vehicle does not require any extra driving force.
  • the vaporised medium After the vaporised medium has passed through the turbine 37 or the bypass line 38 , it is led to a condenser 43 .
  • the medium is cooled in the condenser 43 by coolant in the second cooling circuit to a temperature at which it condenses.
  • the coolant in the second cooling circuit will thus be at a lower temperature than the coolant in the first cooling circuit.
  • the medium is therefore cooled in the condenser 43 to a relatively low temperature before it is again used to absorb thermal energy in the heat exchangers 34 , 9 , 35 , 14 .
  • Said line circuit 32 makes it possible for thermal energy from coolant in the first cooling circuit, the charge air, exhaust gases in the exhaust line and the recirculating exhaust gases to be utilised and converted to mechanical energy to power the vehicle 1 .
  • the combustion engine 2 thus acquires greater capacity and efficiency without being supplied with extra fuel.
  • the cooling action of the medium in the line circuit 32 upon charge air in the second cooler 9 , recirculating exhaust gases in EGR cooler 14 and coolant in the heat exchanger 34 reduces the load on the ordinary coolers 10 , 15 , 20 in their task of cooling these media.
  • the dimensions of the ordinary coolers 10 , 15 , 20 may therefore be smaller.
  • exhaust gases flow through the exhaust line 4 .
  • the exhaust gases drive the turbines 5 of the turbo unit.
  • the turbines 5 are thus provided with driving power which drives the compressor 6 of the turbo unit.
  • the compressor 6 draws in and compresses surrounding air in the inlet line 8 . Compressing the air raises its pressure and temperature.
  • the compressed air undergoes a first step of cooling in the first charge air cooler 9 by the medium circulating in the line circuit 32 and a second step of cooling in the second charge air cooler 10 by coolant circulating in the third cooling circuit.
  • the coolant in the third cooling circuit has, after the cooling in the third cooler 29 , a temperature substantially corresponding to that of the surroundings. This means that the compressed air can likewise be cooled to a temperature close to that of the surroundings in the second charge air cooler 10 .
  • the control unit 13 keeps the EGR valve 12 open so that part of the exhaust gases in the exhaust line 4 is led into the return line 11 .
  • the recirculating exhaust gases undergo in the first EGR cooler 14 a first step of cooling by the medium circulating in the line circuit 32 .
  • the recirculating exhaust gases are thereafter led to the second EGR cooler 15 in which they are cooled by coolant from the third cooling circuit.
  • the recirculating exhaust gases may be cooled to a temperature close to the temperature of the surroundings. Exhaust gases in the return line 11 may therefore undergo cooling to substantially as low a temperature as the compressed air before they are mixed. This means that a substantially optimum amount of compressed air and recirculating exhaust gases can be led into the combustion engine 2 at a high pressure, resulting in the possibility of combustion in the engine 2 with high performance and optimum reduction of the nitrogen oxides in the exhaust gases.
  • the embodiment in FIG. 1 thus uses a first cooling circuit, a second cooling circuit and a third cooling circuit which form part of a common cooling system with a common coolant.
  • Coolant is circulated in the common cooling system by a coolant pump 18 .
  • the coolant may undergo in the common cooling system one, two or three steps of cooling before it is used for cooling.
  • the coolant in the first cooling circuit is cooled in the first cooler 20 before it is used to cool the combustion engine 2 and oil in the oil cooler 22 .
  • the coolant received in the second cooling circuit has undergone a first step of cooling in the first cooler 20 .
  • the coolant then undergoes a second step of cooling in the second cooler 26 before it is used to cool the circulating medium in the condenser 43 .
  • the coolant received in the third cooling circuit has already undergone steps of cooling in the first cooler 20 and the second cooler 26 .
  • the coolant thereafter undergoes a third step of cooling in the third cooler 29 by air at the temperature of the surroundings before it is used to cool the compressed air in the second charge air cooler 10 and the recirculating exhaust gases in the second EGR cooler 15 .
  • FIG. 2 depicts an alternative embodiment of the cooler arrangement.
  • the first cooling circuit constitutes a separate cooling system.
  • This separate cooling system corresponds substantially to a conventional cooling system for cooling a combustion engine 2 .
  • the coolant is circulated in the first cooling circuit by a coolant pump 18 .
  • the coolant in the cooling system cools not only the combustion engine but also oil in an oil cooler 22 .
  • the coolant in the first cooling circuit is cooled in a heat exchanger 34 by the circulating medium and in a first cooler 20 .
  • the second cooling circuit and the third cooling circuit here constitute a joint cooling system with a circulating coolant.
  • a coolant pump 44 circulates coolant in the joint cooling system.
  • coolant After coolant has been cooled in the second cooler 26 , it is led in the second line system 24 to a first condenser 43 in which it subjects to a first step of cooling the medium circulating in the energy-absorbing system. The coolant is thereafter led back to the second cooler 26 for renewed cooling.
  • the third cooling circuit comprises a line system 28 which receives part of the coolant from the second cooler at a location 27 .
  • the coolant received at this location has therefore already been cooled in the second cooler 26 .
  • the coolant is led in the line system 28 to the third cooler 29 which is situated upstream of the second cooler 26 with respect to the direction of air flow through the coolers 26 , 29 .
  • This means that the coolant is cooled in the third cooler 29 by air which is at a lower temperature than the air which flows through the second cooler 26 .
  • the coolant leaving the third cooler 29 is thus at a lower temperature than coolant leaving the second cooler 26 .
  • Coolant in the third cooling circuit is led to a second condenser 45 in which it subjects to a second step of cooling the medium circulating in the energy-absorbing system.
  • the coolant is thereafter led back to the line system 24 of the second cooling circuit at a location 47 and the second cooler 26 in order to be cooled.
  • the medium in the energy recovery system undergoes in this case a first step of cooling in a first condenser 43 by coolant in the second cooling circuit and a second step of cooling in a second condenser 45 by coolant in the third cooling circuit.
  • the circulating medium may thus be cooled to a temperature close to the temperature of the surroundings.
  • Such effective cooling of the medium circulating in the energy recovery system enables it to absorb a relatively large amount of thermal energy which can be recovered in the turbine 37 .
  • the medium in the energy recovery system is used to cool the recirculating exhaust gases in the second EGR cooler 15 .
  • FIG. 3 depicts a further alternative embodiment of the cooler arrangement.
  • the first cooling circuit, the second cooling circuit and the third cooling circuit constitute separate cooling systems.
  • a coolant pump 18 circulates the coolant in the first cooling circuit.
  • This cooling circuit corresponds entirely to the cooling circuit in FIG. 2 .
  • a coolant pump 44 circulates the coolant in the second cooling circuit.
  • the coolant in the second cooling circuit cools the compressed air in the second EGR cooler 10 and the medium in the first condenser 43 .
  • the coolant is thereafter cooled in the second cooler 26 .
  • a coolant pump 46 circulates the coolant in the third cooling circuit.
  • the coolant in the third cooling circuit cools the compressed air in the second EGR cooler 10 and the medium in the second condenser 45 .
  • the coolant is thereafter cooled in the third cooler 29 .

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
US13/699,319 2010-05-25 2011-05-11 Cooler arrangement for a vehicle powered by a supercharged combustion engine Expired - Fee Related US8584457B2 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
SE1050516A SE535877C2 (sv) 2010-05-25 2010-05-25 Kylarrangemang hos ett fordon som drivs av en överladdad förbränningsmotor
SE1050516 2010-05-25
SE1050516-2 2010-05-25
PCT/SE2011/050593 WO2011149409A1 (en) 2010-05-25 2011-05-11 Cooler arrangement for a vehicle powered by a supercharged combustion engine

Publications (2)

Publication Number Publication Date
US20130068202A1 US20130068202A1 (en) 2013-03-21
US8584457B2 true US8584457B2 (en) 2013-11-19

Family

ID=45004187

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/699,319 Expired - Fee Related US8584457B2 (en) 2010-05-25 2011-05-11 Cooler arrangement for a vehicle powered by a supercharged combustion engine

Country Status (9)

Country Link
US (1) US8584457B2 (pt)
EP (1) EP2577016B1 (pt)
JP (1) JP5596855B2 (pt)
KR (1) KR101780367B1 (pt)
CN (1) CN103237967B (pt)
BR (1) BR112012026562A2 (pt)
RU (1) RU2524479C1 (pt)
SE (1) SE535877C2 (pt)
WO (1) WO2011149409A1 (pt)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130042841A1 (en) * 2011-08-17 2013-02-21 GM Global Technology Operations LLC Exhaust gas recirculation system for an internal combustion engine
US20130186087A1 (en) * 2010-07-14 2013-07-25 Mack Trucks, Inc. Waste heat recovery system with partial recuperation
US20170122131A1 (en) * 2014-06-26 2017-05-04 Volvo Truck Corporation Internal combustion engine system with heat recovery
US20180171863A1 (en) * 2016-12-15 2018-06-21 Deutz Aktiengesellschaft Internal combustion engine
US20190003419A1 (en) * 2015-12-21 2019-01-03 Cummins Inc. Integrated control system for engine waste heat recovery using an organic rankine cycle
US20190368383A1 (en) * 2018-03-28 2019-12-05 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Internal combustion engine with evaporative cooling and waste heat utilization
US11124047B2 (en) 2018-11-03 2021-09-21 Hyundai Motor Company Vehicular HVAC system with liquid-cooled charge air cooler integration
US11220931B2 (en) 2017-06-07 2022-01-11 Scania Cv Ab Cooling system for a combustion engine and a WHR system

Families Citing this family (43)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009028467A1 (de) * 2009-08-12 2011-02-17 Robert Bosch Gmbh Vorrichtung zur Nutzung von Abwärme
US8813489B2 (en) * 2011-02-15 2014-08-26 Deere & Company Internal combustion engine charge air cooler precooler
US9803548B2 (en) * 2012-04-02 2017-10-31 Powerphase Llc Gas turbine efficiency and regulation speed improvements using supplementary air system continuous and storage systems and methods of using the same
DE102012209811A1 (de) 2012-06-12 2013-12-12 Bayerische Motoren Werke Aktiengesellschaft Antriebssystem für ein Fahrzeug mit einer Brennkraftmaschine
DE102012209813A1 (de) 2012-06-12 2013-12-12 Bayerische Motoren Werke Aktiengesellschaft Antriebssystem für ein Fahrzeug mit einer Brennkraftmaschine
DE102012209808A1 (de) 2012-06-12 2013-12-12 Bayerische Motoren Werke Aktiengesellschaft Antriebssystem für ein Fahrzeug mit einer Brennkraftmaschine
DE102012216452A1 (de) * 2012-09-14 2014-03-20 Eberspächer Exhaust Technology GmbH & Co. KG Wärmeübertrager
US9017217B2 (en) * 2012-11-08 2015-04-28 Ford Global Technologies, Llc Pilot downshifting system and method
DE102013205648A1 (de) * 2012-12-27 2014-07-03 Robert Bosch Gmbh System zur Energierückgewinnung aus einem Abwärmestrom einer Brennkraftmaschine
US8813691B1 (en) 2013-02-18 2014-08-26 Shawn Grannell High efficiency, ternary mix engine
RU2544115C1 (ru) * 2013-08-23 2015-03-10 Николай Борисович Болотин Двигатель внутреннего сгорания с регенерацией тепла
RU2531460C1 (ru) * 2013-09-27 2014-10-20 Николай Борисович Болотин Двигатель внутреннего сгорания с регенерацией тепла
US9587546B2 (en) * 2013-10-02 2017-03-07 Ford Global Technologies, Llc Methods and systems for hybrid vehicle waste heat recovery
JP2015086779A (ja) * 2013-10-30 2015-05-07 いすゞ自動車株式会社 エンジン冷却システム
JP2015086778A (ja) * 2013-10-30 2015-05-07 いすゞ自動車株式会社 エンジン冷却システム
KR101601088B1 (ko) * 2013-12-23 2016-03-09 현대자동차주식회사 엔진 냉각 시스템
US20150198082A1 (en) * 2014-01-16 2015-07-16 GM Global Technologies Operations LLC Turbocharged Internal Combustion Engine With Pre-Charge Air Cooler
JP6194273B2 (ja) * 2014-04-04 2017-09-06 株式会社神戸製鋼所 排熱回収装置及び排熱回収方法
JP6194274B2 (ja) * 2014-04-04 2017-09-06 株式会社神戸製鋼所 排熱回収システム及び排熱回収方法
KR101575254B1 (ko) * 2014-05-20 2015-12-07 현대자동차 주식회사 차량 엔진 냉각 시스템
EP3161275B1 (en) * 2014-06-26 2018-12-19 Volvo Truck Corporation A waste heat recovery device
JP6342755B2 (ja) * 2014-09-05 2018-06-13 株式会社神戸製鋼所 圧縮装置
DE102014220334A1 (de) * 2014-10-07 2016-04-07 Krones Aktiengesellschaft Lebensmitteltechnische Prozessanlage, insbesondere Brauereianlage mit Blockheizkraft
DE102014017244A1 (de) * 2014-11-20 2016-06-09 Man Truck & Bus Ag Kühlsystem für ein Fahrzeug, insbesondere für ein Nutzfahrzeug
DE102014017245A1 (de) * 2014-11-20 2016-06-09 Man Truck & Bus Ag Kühlsystem für ein Fahrzeug, insbesondere für ein Nutzfahrzeug
SE538836C2 (en) * 2014-12-05 2016-12-20 Scania Cv Ab A cooling arrangement for a WHR system
US9863306B2 (en) * 2015-01-26 2018-01-09 Delphi Technologies, Inc. Engine restart aid
KR102403512B1 (ko) 2015-04-30 2022-05-31 삼성전자주식회사 공기 조화기의 실외기, 이에 적용되는 컨트롤 장치
US10202888B2 (en) * 2015-12-08 2019-02-12 Ford Global Technologies, Llc Engine air path cooling system
SE540089C2 (en) * 2016-07-07 2018-03-20 Scania Cv Ab A cooling system in a hybrid vehicle
SE540324C2 (en) * 2016-10-28 2018-06-26 Scania Cv Ab A cooling system for cooling a combustion engine and a WHR system
DE102017011844A1 (de) * 2017-12-21 2019-06-27 Daimler Ag Anordnung zur Umwandlung thermischer Energie aus Verlustwärme einer Verbrennungskraftmaschine
DE102017011851A1 (de) * 2017-12-21 2019-06-27 Daimler Ag Anordnung zur Umwandlung thermischer Energie aus Verlustwärme einer Verbrennungskraftmaschine
US20190234343A1 (en) * 2018-01-30 2019-08-01 International Engine Intellectual Property Company, Llc. Organic rankine cycle waste heat recovery system having two loops
FR3079558B1 (fr) * 2018-03-27 2023-11-03 Renault Sas Circuit de refroidissement pour un moteur a combustion interne equipe d'un circuit de recirculation de gaz d'echappement et son procede de commande
DE102018113395A1 (de) * 2018-06-06 2019-12-12 Man Energy Solutions Se Kühlsystem einer Brennkraftmaschine
US10830122B2 (en) 2018-10-29 2020-11-10 Fca Us Llc Intake and charge air cooling system
KR102079584B1 (ko) 2019-04-30 2020-02-20 김영재 기능을 확장할 수 있는 조리 용기
FR3101917B1 (fr) * 2019-10-09 2022-07-15 Ifp Energies Now Système de refroidissement à radiateur unique
EP4127420A4 (en) * 2020-03-23 2024-01-24 Cummins, Inc. MULTI CORE HEAT RECOVERY CHARGE COOLER
AT524156B1 (de) * 2020-08-04 2022-07-15 Man Truck & Bus Se Vorrichtung zur Energierückgewinnung mit einem Abwärmenutzungskreislauf
KR20220080556A (ko) * 2020-12-07 2022-06-14 현대자동차주식회사 차량의 통합열관리 시스템
US11680515B1 (en) 2022-03-31 2023-06-20 Fca Us Llc Intake and charge air cooling system with passive variable charge enabler

Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3888084A (en) * 1974-05-20 1975-06-10 Gilbert L Hawkins Thermal recovery system
DE19854544A1 (de) 1998-11-26 2000-06-08 Mtu Friedrichshafen Gmbh Kühlsystem für eine aufgeladene Brennkraftmaschine
US20080264609A1 (en) * 2007-04-26 2008-10-30 Behr Gmbh & Co. Kg Heat exchanger for exhaust gas cooling; method for operating a heat exchanger; system with a heat exchanger for exhaust gas cooling
US20090020079A1 (en) * 2005-11-10 2009-01-22 BEHRmbH & Co. KG Circulation system, mixing element
GB2453218A (en) 2007-09-25 2009-04-01 Ford Global Tech Llc Internal combustion engine cooling system
DE102007052117A1 (de) 2007-10-30 2009-05-07 Voith Patent Gmbh Antriebsstrang, insbesondere für Lkw und Schienenfahrzeuge
US20090211253A1 (en) 2005-06-16 2009-08-27 Utc Power Corporation Organic Rankine Cycle Mechanically and Thermally Coupled to an Engine Driving a Common Load
US20100012054A1 (en) 2006-09-22 2010-01-21 Renault Trucks Cooling circuit for the thermal engine ofan automotive vehicle
US7874154B2 (en) * 2006-09-20 2011-01-25 Man Nutzfahrzeuge Oesterreich Ag Cooling system of an internal combustion engine having charge air feed
US20110198070A1 (en) * 2010-02-12 2011-08-18 C.R.F. Societa Consortile Per Azioni Motor-vehicle with an auxiliary cooling system including one or more radiators constituted by vehicle body components
US20110214627A1 (en) * 2010-03-03 2011-09-08 Denso Corporation Controller for engine cooling system
US8028522B2 (en) * 2005-09-06 2011-10-04 Behr Gmbh & Co. Kg Cooling system for a motor vehicle
US8434307B2 (en) * 2009-01-31 2013-05-07 Modine Manufacturing Company Exhaust gas system and method for recovering energy

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH627524A5 (de) * 1978-03-01 1982-01-15 Sulzer Ag Verfahren und anlage zur waermenutzung durch waermeentzug aus mindestens einem stroemenden waermetraeger.
CH632051A5 (de) * 1978-10-25 1982-09-15 Sulzer Ag Brennkraftmaschinenanlage.
FR2449780A1 (fr) * 1979-02-22 1980-09-19 Semt Procede et dispositif de recuperation d'energie thermique dans un moteur a combustion interne suralimente
JPS61151039U (pt) * 1985-03-11 1986-09-18
FR2757903B1 (fr) * 1996-12-31 1999-03-26 New Sulzer Diesel France Sa Procede et installation de recuperation de chaleur dans de l'air de suralimentation d'un moteur
DE10335567A1 (de) * 2003-07-31 2005-03-10 Behr Gmbh & Co Kg Kreislaufanordnung zur Kühlung von Ladeluft und Verfahren zum Betreiben einer derartigen Kreislaufanordnung
DE102004024289A1 (de) * 2004-05-15 2005-12-15 Deere & Company, Moline Kühlsystem für ein Fahrzeug
US8806881B2 (en) * 2004-12-23 2014-08-19 Valeo Systemes Thermiques System for controlling the thermal energy of a motor vehicle engine by adjusting the fluid actuators of said system
DE102006028868B4 (de) * 2006-06-23 2017-07-13 Man Truck & Bus Ag Aufgeladene Brennkraftmaschine mit einer Expandereinheit in einem Wärmerückgewinnungskreislauf
AT507096B1 (de) * 2008-12-10 2010-02-15 Man Nutzfahrzeuge Oesterreich Antriebseinheit mit kühlkreislauf und separatem wärmerückgewinnungskreislauf

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3888084A (en) * 1974-05-20 1975-06-10 Gilbert L Hawkins Thermal recovery system
DE19854544A1 (de) 1998-11-26 2000-06-08 Mtu Friedrichshafen Gmbh Kühlsystem für eine aufgeladene Brennkraftmaschine
US20090211253A1 (en) 2005-06-16 2009-08-27 Utc Power Corporation Organic Rankine Cycle Mechanically and Thermally Coupled to an Engine Driving a Common Load
US8028522B2 (en) * 2005-09-06 2011-10-04 Behr Gmbh & Co. Kg Cooling system for a motor vehicle
US20090020079A1 (en) * 2005-11-10 2009-01-22 BEHRmbH & Co. KG Circulation system, mixing element
US7874154B2 (en) * 2006-09-20 2011-01-25 Man Nutzfahrzeuge Oesterreich Ag Cooling system of an internal combustion engine having charge air feed
US20100012054A1 (en) 2006-09-22 2010-01-21 Renault Trucks Cooling circuit for the thermal engine ofan automotive vehicle
US20080264609A1 (en) * 2007-04-26 2008-10-30 Behr Gmbh & Co. Kg Heat exchanger for exhaust gas cooling; method for operating a heat exchanger; system with a heat exchanger for exhaust gas cooling
GB2453218A (en) 2007-09-25 2009-04-01 Ford Global Tech Llc Internal combustion engine cooling system
DE102007052117A1 (de) 2007-10-30 2009-05-07 Voith Patent Gmbh Antriebsstrang, insbesondere für Lkw und Schienenfahrzeuge
US8434307B2 (en) * 2009-01-31 2013-05-07 Modine Manufacturing Company Exhaust gas system and method for recovering energy
US20110198070A1 (en) * 2010-02-12 2011-08-18 C.R.F. Societa Consortile Per Azioni Motor-vehicle with an auxiliary cooling system including one or more radiators constituted by vehicle body components
US20110214627A1 (en) * 2010-03-03 2011-09-08 Denso Corporation Controller for engine cooling system

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
International Search Report mailed Sep. 1, 2011 in corresponding PCT International Application No. PCT/SE2011/050593.

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130186087A1 (en) * 2010-07-14 2013-07-25 Mack Trucks, Inc. Waste heat recovery system with partial recuperation
US8919123B2 (en) * 2010-07-14 2014-12-30 Mack Trucks, Inc. Waste heat recovery system with partial recuperation
US20130042841A1 (en) * 2011-08-17 2013-02-21 GM Global Technology Operations LLC Exhaust gas recirculation system for an internal combustion engine
US9353670B2 (en) * 2011-08-17 2016-05-31 GM Global Technology Operations LLC Exhaust gas recirculation system for an internal combustion engine
US20170122131A1 (en) * 2014-06-26 2017-05-04 Volvo Truck Corporation Internal combustion engine system with heat recovery
US10378390B2 (en) * 2014-06-26 2019-08-13 Volvo Truck Corporation Internal combustion engine system with heat recovery
US20190003419A1 (en) * 2015-12-21 2019-01-03 Cummins Inc. Integrated control system for engine waste heat recovery using an organic rankine cycle
US10724471B2 (en) * 2015-12-21 2020-07-28 Cummins Inc. Integrated control system for engine waste heat recovery using an organic Rankine cycle
US20180171863A1 (en) * 2016-12-15 2018-06-21 Deutz Aktiengesellschaft Internal combustion engine
US10619558B2 (en) * 2016-12-15 2020-04-14 Deutz Aktiengesellschaft Internal combustion engine
US11220931B2 (en) 2017-06-07 2022-01-11 Scania Cv Ab Cooling system for a combustion engine and a WHR system
US20190368383A1 (en) * 2018-03-28 2019-12-05 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Internal combustion engine with evaporative cooling and waste heat utilization
US11008899B2 (en) * 2018-03-28 2021-05-18 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Internal combustion engine with evaporative cooling and waste heat utilization
US11124047B2 (en) 2018-11-03 2021-09-21 Hyundai Motor Company Vehicular HVAC system with liquid-cooled charge air cooler integration

Also Published As

Publication number Publication date
RU2012156162A (ru) 2014-06-27
KR20130081664A (ko) 2013-07-17
US20130068202A1 (en) 2013-03-21
KR101780367B1 (ko) 2017-09-21
WO2011149409A1 (en) 2011-12-01
JP5596855B2 (ja) 2014-09-24
SE535877C2 (sv) 2013-01-29
CN103237967A (zh) 2013-08-07
SE1050516A1 (sv) 2011-11-26
EP2577016A1 (en) 2013-04-10
EP2577016A4 (en) 2018-01-24
EP2577016B1 (en) 2019-02-27
RU2524479C1 (ru) 2014-07-27
BR112012026562A2 (pt) 2016-07-12
JP2013526682A (ja) 2013-06-24
CN103237967B (zh) 2016-02-10

Similar Documents

Publication Publication Date Title
US8584457B2 (en) Cooler arrangement for a vehicle powered by a supercharged combustion engine
EP2678548B1 (en) System for converting thermal energy to mechanical energy in a vehicle
US8490392B2 (en) Arrangement for a supercharged combustion engine concerning coolers for inlet air to and exhaust gases from the engine
US20110139131A1 (en) Arrangement for a supercharged combustion engine concerning coolers for inlet air to and exhaust gases from the engine
CA2451509C (en) Temperature control for turbocharged engine
US9341087B2 (en) Arrangement and method for converting thermal energy to mechanical energy
EP2959145B1 (en) System for recuperating heat from the exhaust gases in an internal combustion engine, with two heat exchangers on a gas recirculation circuit
US7040303B2 (en) Combined aftercooler system with shared fans
US9074492B2 (en) Energy recovery arrangement having multiple heat sources
JP2005517857A (ja) 自動車のエンジンに送られる気体の温度を制御する方法及び気体の温度を調節する装置
JP2011503436A (ja) 過給燃焼機関の構成
EA019697B1 (ru) Установка для охлаждения двигателя
CN110439666B (zh) 具有两个温控器、包括处于朗肯循环中的闭合回路的发动机冷却系统
US20110088671A1 (en) Exhaust gas recirculation cooler system
US5875633A (en) Cooling system for internal combustion engines
WO2011136717A1 (en) Arrangement for cooling of compressed air and/or recirculating exhaust gases which are led to a combustion engine

Legal Events

Date Code Title Description
AS Assignment

Owner name: SCANIA CV AB, SWEDEN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:KARDOS, ZOLTAN;KLINGBERG, KRISTOFFER;SIGNING DATES FROM 20121024 TO 20121031;REEL/FRAME:029334/0387

STCF Information on status: patent grant

Free format text: PATENTED CASE

FPAY Fee payment

Year of fee payment: 4

FEPP Fee payment procedure

Free format text: MAINTENANCE FEE REMINDER MAILED (ORIGINAL EVENT CODE: REM.); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

LAPS Lapse for failure to pay maintenance fees

Free format text: PATENT EXPIRED FOR FAILURE TO PAY MAINTENANCE FEES (ORIGINAL EVENT CODE: EXP.); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

STCH Information on status: patent discontinuation

Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362

FP Lapsed due to failure to pay maintenance fee

Effective date: 20211119